Balanced ball type vane pump or motor



July 3l,A 1945. G. A. WALDIE 2,380,885

BALANCD BALL TYPE VANE PUMP OR MOTOR Filed Dec. 18, 1941 l 4 sheets-sheet 1 b n1 g la 8 'l 3 in z 24 2.5/ 2' o `2.1 u .l @o L z 1 z 26 nf I :aa 2.9 MAIN Axis oF La PLQ/PING: CHAMBER.

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4 Sheets-Sheet July 3l, 1945. G. A. WALDIE BALANCED BALL TYPE VANE PUMP OR MOTOR Filed Dee. 1s, 1941 JTEJ? July M, i945. G. A. WALDIE BALANCED BALL TYPE VANE PUMP OR MOTOR Filed Dec. 18, 1941 4 Sheets-Sheet 5 ATmEYS July 31 1945.

Filed Dec.

BALANCED BALL TYPE VANE PUMP OR MOTOR WALDIE 4 Sheets-Sheet 4 E'llr. 14

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A@ INVENTOQ GEOQG A. WLDIE u fw-Lu,

i ATTmEYS `Paiented July 3 1', 1945 UNITED STAT-Es PATENT OFFICE 1.3,888 l BALANCID MIL m VANI PUMP R GeorgeLWamFranklimOhimaaalgnoi-tolhe t Corp. lne., Mount Gilllyilranlie will!!! cad, 0hio, a a! Delaware Application December 1s. mi, serial No. 423.486 s einen. im. isa-m) the following speciileation 'is read in connection with the accompanying drawings.

In the drawings:

Figure 1 is s view ci s minimaalV meier and l pump mechanism showing the motor in elevation and the Dump in section.

Figure 2 is a section of the pump taken alona thelinel-linlilurel.'

Figure 3 is a vertical section tiiken ailongthe connai surfaces of ine wing sus mi by hyiounes-sofngurei draulic pressure produced by a pump. In the case of a pump. the pressure is instantaneously available for fast control. whereas in the case of control exercised by an electriomotor the energy Fllure 4 shows a modined form of the im' proved pump including the use oi' ball bearings instead of vroller bearings for rotatably supporting the rotor.

of the motor is not available until the motor shall Figure 5 is a section taken .along the line have come up to speed. The main disadvantage p o! the prior-srt pumps. when use in this particular connection, is the weight and bulk of the pump. particularly when the p'ump must handle large quantities of pressure fluid to exercises coni0 siderable number of control functions. perhaps simultaneously.

The primary obiect of the present inventionfis to provide a pump which can handle large quantitles of fluid at high pressure. auch as oil, and u ina chamber and rotor to show the action ofthe' yet is of comparatively small sise. Prom one as' peet. therefore, the invention contemplates a pressure pump which has a high volumetricfluid capacity, as compared to its sise.

Another object is to provide a pump of this character, in which the prime mover which ac-- tuates the pump (usually an electric motor) will rotate in the same direction, but delivery at the versing valves so that the reversal of flow is ac-f complished within the pump.

A further object is to provide a pump which may bel made of relatively fewupartsieasily ina-` chlned, and of light weight when desired-aud- 40 which can be readily assembly and disassembled for inspection purposes.

'miese einem are attaincdin brief, by providing Aa closed compartment formed of blocks oi any suitable material having tapered. active surfaces, and by rotating a rotor within the com. pertinent in such a manner that the space on each side of the rotor lsdivided'by the rotor blades into suction and pressure chambers. The

l-l in Figure 3.

Figure 8 ls a-perspective view of the rotor.- showing the movability of the blades with reapect to the rotor disc or web.

Figure 'l is a fragmentary corner view of the pump block, showing one of the passageways leading from the pumping chamber to the exterior port.

Figure 8 is a developmental view of the pumpareas.

ll'lirure 9 is a diagrammatic .view of the improved pumpto illustrate the directions in which the direction of the reacting thrust which must be provided at the bea Figure l0 is a top perspective view of the pump.

. pump can be reversed without 'the use of re- 35 'm1 the Wbm muon puuy'nmond t.

enneiin which me porucnsof the pump meer are tapered. v

Figure il is a vertical sectional view of a inodformv oi' the e forlreversing the direction of flow 12. sectional view taken along the Il inllzure 13.

.istl view takenalongtheline iii-i4 in 12J. e. withthe right-hand bolted cover member of ligure 12 removed to, expose the worm andgeartrheelmechaniam. lniFlgurelethe' blocks may be rotated or rocked about an axis: han@ wheel which' operates the worm gear and singularly disposed with respect to the axis of the rotor shaft to changethe suction and pressure action of the various parts of the rotor and thus to reverse the direction of huid delivery.

The invention will be better understood wh u primemover 8, which is usually un electric motor;

the wenn gwi' are shown in velieviitioiizi.`

l Referring more particularly to Figure l, reierenee numeral i generally demi-nuten the improved pump from which a driving inhalt 2 extends into u.

improved pump, in which provimuren. 8 is a sectional view teken man; ine

2 f 'rae improved' pump 1 is constituted essentially o:

I, I, and I,- secured our or more bolts 1.

' weight is of termediate block I is provided ing II, which constitutes the pump chamber, this surfaces being preferably machined and extending substantially parallel to one another. These surfaces are spaced apart by the intermediate block I which, if desired, may form an integral portion oi' either of the two outer blocks. 'This intermediate block is cut on the bias so that when the blocks I, I and I are assembled the outer surfaces or the blocks I and I extend in parallel directions. but the surfaces I and I extend diagonally across the combined block unit. Ihe inyith a large openopening being of circular configuration. as shown in Flgure`3, and having a curved vperiphery indicated at II, for reasons which will be explained hereinafter. The main axis of the chamber has been indicated in Figure 1, and as shown is positioned at an angle with respect to the main axis of the motor.

The block I is provided with a pair of, arcuate shaped slots, shown at I2, II, these slots being' arranged about a circle which is preferably concentric with the main axis of the pump, the end of one slot terminating at a considerable distance from the end of the adjacent slot so that the two slots are not interconnecting. The width and depth of these slots depend on the amount of fluid to be-accommodated, and a section taken through the slots may show a semicircle or a rectangle. As will be explained hereinafter, these slots alternate as pressure and suction ports for the fluid which has been forced into or withdrawn from the slots by a rotating rotor, the details of which will be described presently. i

In order to admit fluid into the pump chamber II through the slots II, II, ported openings II, It are provided, these openings passing all the way through the block I and the intermediate block I, and terminating at a position just below the tapered surface I of the block I. The openings II, II communicate with tubings II, I1, one of which passes -into the fluid supply tank (not shown), depending on the direction in which the pump is deliveringi'iuid, and the other is taken to the position at which work is to be performed. This work may consist, for example. of moving an aileron or other control surface of an airplane (not shown), in which-case the fluid pressure could be translated into a reciprocatory movement by a plunger and cylinder mechanism.

The right-hand blockA I (Figure l) is provided with a pair of slots or grooves II, II. similar to .those formed in the block I, and the general arrangement is such thatthe slot II in block I, on one side of the rotor, is connected through one ofthe ports II, Il with the slot II in the other block on the opposite side .of the rotor. The remaining slot II'of the first-mentioned block is connected through the other of the ports II, II to the other slot II on the opposite side of the rotor. In other wor the diagonally positioned slots onl the opposite sides of the rotor are connected together, and' each pair communiuaed to advantage. In case weight f is not important,

cates respectively with'tbe pcrtsII. II. munication is made between the various II, II and their respective porta II, II 'passageways II shown more clearoin I lalthough the vpassageway! are shown wayofdottedlinesinmguresiandI.

blocks 4,' s from the ports u, is,

)upwardly to reach the slots II, II. The reason "f for this arrangement will .be clear when the rotor structure and its operation have been described.

l 'Construction o! the rotor 'Ihe rotor forms a continuation of the main driving shaft 2 and takes on a spherical configuration, as indicated at II. HubsV II extend laterally from opposite sides of the rotor, the leftandthe right-hand hub terminating in a shaft portion II. The blocks I'and I are provided with openings II and II, respectively, which loosely receive the hubs II. these openings terminating at their outer ends in countersunk bores,

'so a pair ofoppositelypositioned roller bearings II, II for rotatably supporting the rotor.

Ihe blocks I and I are provided with recesses of a partial spherical shape to conform to the shape of the spherical rotor and to permit the I5 rotor to rotate between the blocks when the. motor I is energized. The central or spherical portion of the rotor is provided with a radially extending and vertically directed web II ywhich extends around the sphere II as an annular ring. and preferably is formed integral with the sphere. The-web and sphere may be formed of any hard wearing material, such as metal or certain types of plastics, and in case weight is an important consideration the metal may bea magnesium or aluminum alloy. It will be noted from Figure 1 that the size ,and position of the pumping chamber II and the positional relationship of the annular web I I are auch that the outermost peripheral-edges on opposite sides of the web II coincide with the' jointformed between each arcuate shaped surface,"v and the tapered surfaces I and I of the two blocks.

The annular ring II is provided with a plurality of radially extending slots II (six as shown) and illustrated more clearly in Figure 6, these slots extending inwardly as far as the peripheral surface II. These slots snugly but slidably receive the vanes or blades Il, these blades being formed of a`tough, long-wearing material and are'preferably machined on all sides. It will be noted that the width of each blade is considerably greater than the vertical depth (Figure I) of the ring 30. The blades take the form generally of 65 a rectangle, but their inner edges are curved Aboth in the vertical and horinontal directions to conform with the spherical shape of the element II. The outer vertical edges are curved in the vertical and horizontal directions to conform tothe arcuate shape of the surface II (Figure 1) and also to the circular configuration of the chamber II as shown in Figure 3. 'I'he wp and bottom 4edges of each blade are also given a convex curvature to accommodate vthe blade to the tapered surfaces'I, I as the rotor is rotated.

Operation When the motor I (Figure l) is energized and the shaft 2 rotated, the rotor I9,l together with the ,annular ring 30, is also caused to rotate vwithin the chamber i8. Due to the fact that the therefore drawn through that conduit Il or I 'l which communicates with this space through one of the annular slots I2 in the .block l, and also through one of the yslots Il in the other block i. These slots, of which there are two in each block as shown in Figure 3, are diagonally connected together to `form pairs, and when one pair is functioning as an inlet port the other pair will be operating as an outlet port. Thus fluid is drawn into,` the larger spaces between the ring 30 and the tapered surfaces 8 and 9 ofthe pump blocks through one of the ports' H, I5 and the As the rotor continues to rotate, that body vpassageways I8, into one of the pairs of slots of fluid contained between an adjacent pair of blades 32 tends to be squeezed into the smaller space 33 (Figure l) because, as pointed out hereinbei'ore, each vane I2 is caused to move either to the right or left as the annular ring is rotated. The .duid in the-small space 33 is therefore forced outwardly through vone of the diagonally positioned pairs of slotsv l2, il and through the suitably positioned passagways Il', into the outlet port I 4 or I5. depending on the direction of rotation and the instantaneous positional relay tionship between these ports, their communicating passageways and the pumping or suction portions of the pumping chamber.

This operation is shown most clearly in developmental Figure 8, which illustrates the manner in -which the blades a to f, inclusive, all take different sphere la during operation of the pump. Assuming, for example, that the upper right-hand space g and the lower left-hand space h of the pump chamber I0 are momentarily pressure chambers, the pressure of the fluid can be resolved into forces indicated at a which act in the horizontal direction against opposite sides of the ring 30, and also forces indicated at It which opcrate in a direction toward the center of the sphere. The forces k tend to balance one another out so that no thrust is caused thereby at the bearings, but the forces y' cause a rotating moment about the center of the sphere, and as illustrated in Figure 9, this rotating force would cause the rotor to turn in the counterclockwise direction. The net result of, all of these forces is that there is 'a thrust downwardly, indicated at l at the left-hand bearing, and a thrust m which operates upwardly at the right-hand bearing. These thrusts, of course, can be readily ac'- commodated by the bearings. It will be noted that there is no `resultant end thrust, so that the bearings for the shaft need not be of the expensive roller type but instead can be of the ordinary ball bearing type. Such a modification is shown in Figure 4, in which the ball bearings 34 replace the-roller bearings shown in Figure 1, and since there is no end 'thrust 4it requires only a. little effort to hold the ball bearings in place longitudinally. In fact, a mere end closure plate 35, screwed tot he blocks l, 6 will suffice.

Due to the fact that the rotor is well balanced, not only from the static but also the dynamic force standpoint, the rotor may be turned at very fast speeds and the output of the pump would be limited only by the volume of the pumping chambers g, h (Figure 9), which in turn, is a measure of the distance between the blocks l, t and the width of the rings 30. It is apparent that inasmuch as the blades 32are only slidably held within the ring 30, these blades can be readily replaced. There is no welding, bolting ,or other'expensive labor to be performed in positioning these blades with respect to the web 3U. The blocks 4, 8 canbe taken-apart merely by removing the boltsl l, and the arrangementv is such (Figure 1) that the rotor I 3 does not even have to be removed from the shaft 2 in order to inspect the condition of the blades and of the tapered surfaces 8 and 9.

When it is desired to reverse the direction of ilow at the .delivery end, it is only necessary to reverse the 'direction of rotation of the rotor at the motor d. However, as will be explained presently, the pump may be modified in such a wayas to reverse the direction of delivery while perl mitting the motor 3 to continue to run in the sure effects, is also clearly shown in Figure 8, and

it is .apparent that each diagonally positioned pair of slots permanently functions either for suction or pressure as long as the rotor is rotated in the same direction, but will reverse its func-` tion when the rotor is rotated in the opposite direction. A study of Figure 8 will also indicate the reason for curving the upper and lower edges of the blades a to j because, as these'blades move across the tapered surfaces l, different points throughout the thickness of each blade will conf same direction. There is shown in Figures 11 to 14 a reversible pump of this character. In general, the construction is such that thechamber which had been momentarily exerting a pressure en'ect when the rotor is turned' and the pumping chamber extends at Va definite angle with respect to the rotor shaft, vnow becomes an exhaust or suction chamber when the pumping ,chamber extends at an opposite angle with remade for rotating the casing about a horizontal axis and to provide an improved port arrangement by which the pump casing can be rotated. The casing is provided at its right-hand end, as seen in Figure 12, with a multi-shouldered shaft 3l which is threaded at one end to receive a thumb nut 3l rotatably secured to a conduit 40. the purpose 'of which will be explained hereinafter. A worm gear II isv ilxedly secured to the shaft by a nut 42, this worm gear being spaced from -the pump casing by a bearing bushing 43. -The latter is journalled in a. plate Il, provided with a flanged leg l5. A cover plate is bolted as at 41 to the i plate II, this cover plate leaving exposed only a portion of the worm gear II. A screw I8 carried'on a rod l! is adapted to mesh with the worm gear II when vthe rod is rotated by the hand wheel 50.

At the opposite side the pump casing terminates in'a multi-shouldered shaft 5I, which is journalled through a bushing 2 in an upstanding plate 52. The shaft 5I carries screw threads which receive a thumb nut 5l, the latter rotatably carrying a conduit 55. It is apparent that when the hand wheel. is rotated the worm gear Il, which is rigidly fixed. to the shaft ,33, will cause the pump casing to be rotated around a horizontal axis which extends through the journals 42, 52. In" order to provide for the inlet and outlet ports which communicate with the pressure and suction chambers on opposite-sides of the rotor through the arcuate slots I2, I3 (Figure 3), holes 56 are drilled in line with the openings in the conduits 4l. l5 and therefore along the axis 0f rotation. These openings communicate with openings 5l which extend outwardly and communicate with the' horizontal openings 58. The latter connected to the slots I2, Il by the passage'- ways I8, which are most clearly .shown in Figure 7.' In order lto facilitate the formation of the holes i1, 5I, these may be drilled from the side and outer surfaces of the pump casing and the excess length of the openings tapped and illled by a set screw II. Consequently, as the hand wheel 5l is rotated to move the pump casing from one side of the vertical axis to the other side, the pumping cavities of the chambers on both sides of the rotor web undergo reversals of function. The pressure cavities will exert a suction effect and the suction cavities will exert a pressure effect so that the passage of iiuid through the pump is completely reversed, notwithstanding the fact that the shaft 2 continues to rotate in the same direction.

It is apparent fromv a consideration of Figure 2,sao,ese

being positioned normally thereto, as in the case oi' Figure 1. But thev general operation of the rotor within the chambers formed between the blocks is similar to that described in connection with Figure 1, so that no additional description of y the details is necessary.

When the pump casing, foi-example, is canted to the left, as shown in-Figure ll, let us assume that the position ,of the ports and of the interconnected pair of slots I2, I3 on opposite sides of the rotor and the remaining interconnected pair of slots I2, Ilis such that the pump delivers pressure fluid at the conduit I0. However, when the pump casing is given a cant to the right by the wheel it, pressure fluid will now be delivered at the conduit 55, assuming that the shaft 2 is being rotated in the same direction as before. Consequently, the hand wheel 50 serves as a means for reversing the now of deliveryof the pump.'

This 'arrangement may be advantageous in those cases where an electric motor is designed to operate more eillciently in one direction than in the other, and also to save lthe cost of a reversing switch in the motor circuit. It is further apparent that inasmuch as the motor never stops during the reversal of the fluid delivery, the ilow of the fluid is available immediately. This would not be true in case the electric motor were reversed, because a definite time would elapse to dstop the motor and then to start the motor in the reverse direction, and during this time the pump would not be delivering fluid at its predetermined pressure.

In Figure 14 there is shown a mechanism by which the pump casing can be automatically moved toits neutral or no-delivery position without sacrificing the non-reversible character of the mechanical connection between the control wheel N and the pump swinging mechanism. Reference numeral Il designates any 'suitable and well known form of device which responds to any type oi' impulse, pneumatic, electrical or mechanical, as for example, when the back pressure developed at the pump becomes excessive or when the device ll is' actuated by the platen oi' a press supplied with fluid from the pump. Under the conditions of excessive back pressure, or when the platen has reached a predetermined position, the device Il may be actuated in any suitable manner to move a rack Il and thus to rotate the worm 4l.

In other words, thegear II, shown in Figure 14.

lithat only a small rotary'movement of the pump is necessary to reverse the pressure and suction effects of the pumping cavities formed between the vanes I2 and the casing blocks DI, 82,.

In order that the pump casing may be moved in the lateral direction with respect to the rotor,

` the intermediate block ilwhich corresponds to the block i in Figure l, is given substantially paralici sides, and the blocks 0I, I2 are also given a corresponding shape. Actually, only the abutting surfaces of the blocks CI, l2 are arranged may be operated either manually at the wheel Il or. vautomaticellv in response to any desired form of impulse operating on the device II. This device may even be a time-operated relay which would serve to cut of! the pump at any given predetermined time of the day or night,l and vice versa. The device ll may also be employed to start the pump in 'one or the other direction, as may be desired at any predetermined time.

In the reversing form of pump as shown in Figures 11 to 14, the taper of the pump chamber may be changed from one side to the other by merely rotating the pump casing about a lateral axis with respect to the rotor, thusv simultaneously reversing the action of all of the spaces contained be- 'parallel because the sides of the pumping chamber directly adjacent the rotor web are given inwardly extending flared portions, as indicated at I3. These portions serve to lengthen the distance indicated at Il over which leakage would have to take place between the blocks II, I2 and the peripheral surface of the sphere Il.v The pump casing in Figure 1l is always positioned at an angle with respect to the rotor shaft instead of tween the blades of the rotor.

While I have described my invention as pertaining to a relatively small pump, such forexample as may be used for control purposes in an airplane or other place where space is at a prepumps, for example those pumps which may be aseaase visable to cast the rotor I9 with a hollow interior,

because obviously the shell of the spherical portion need not be thick, due to the self-supporting action inherent in a sphere.

It will be understood that I desire to comprehend within my invention such modifications as come within the scope of the claims and the in.

l thereabout and extending in the direction of the shaft, inlet and outlet conduits in communication with opposite sides of the pumping chamber, each of said conduits extending over a distance subtended by at least three adjacent vanes, said l rotor having -a spherical portion, said-chamber having an arcuateiy curved outer peripheral wall whose center is removed from the center of said rotary shaft and curved side walls, each vane having inner and outer vedges curved both in vertical and horizontal directions to conform to the spherical portions of said rotor and outer chamber wall, and side edges convexly curved to con` tinuously contact the curved side walls ci said chamber.

2. In a 'fluid pump having a housing which forms a pumping chamber, a rotor mounted on a shaft therein, the walls of said chamber being parallel and extending at an angle other than normal with respect to the axis of the shaft, a plurality of pairs of vanes slidably received by the rotor and arranged equidistantly thereabout, said varies extending in the direction of the shaft, said rotor having a spherical portion, said chamber having an arcuately curved outer peripheral wall whose center is removed from the center of said rotary shaft and curved side walls, each vane having inner and outer edges curved both in vertical and horizontal directions to conform' to the spherical portions of said'rotor and outer chamber wall, and side edges convexly curved to continuously contact the curved side walls of said chamber. y

3. In a fluid pump having a housing which forms a pumping chamber, a rotor mounted on a shaft therein and adapted slidably to receive a plurality of vanes extending longitudinally of the shaft and equidistantly positioned about the rotor, the interior surface of said chamber having a configuration such that when the rotor is turned the vanes slide with respect to the rotor from one side of the chamber to the other side and independently of one another, said rotor having a spherical portion, said chamber having an i arcuately curved outer peripheral wail whose center is removed from thecenter of said rotary shaft and curved side' walls, each vane having inner and outer edges curved both in vertical and horizontal directions to conform to the spherical portions of said rotor and outer chamber wall, and side edges convexly curved to continuously contact the l'curved side walls of saidchamber.

4. In a fluid pump having a housing which y forms a pumping chamber, a rotor mounted on a shaft therein, said chamber having a symmetrical shape in cross-section and the line of symmetry extending at an angle other than normal with respect to the axis of the shaft, a plurality of pairs of vanes slidably received by the rotor, said vanes extending in the direction of the shaft and equidistantly positioned about the rotor, the sliding movements of said vanes within the rotor being independent of one another and determined solely by the changing shape ofthe pumping chamber as the rotor is turned, said rotor having' a spherical portion, said chamber having an arcuately curved outer peripheral wall whose center is removed from the center 0i.' said rotary shaft and curved side walls, each vane having inner and outer edges curved both in verti cal and horizontal directions to conform to the spherical portions of said rotor and outer chamber wall, and side edges convexly curved to continuously contact the curved side walls of said alignedopenings to receive a shaft carrying the rotor, the joints between said outer blocks and intermediate block extending in parallel planes angularly positioned with respect to the axis of the shaft whereby the pumping chamber is arranged at anangle with respect to the rotor, a plurality of pairs of vanes slidablyreceived by the rotor and extending in the direction of the shaft,` said vanes having la width substantially equal to the thickness of the pumping chamber as determined by the thickness of said intermediate metal block, an inlet conduit formed in one of said outer blocks and being effectively in communication with the pumping chamber, and an outlet conduit formed in the same outer metal block as the inlet conduit and being eectively in communication with the pumping chamber, said rotor having a spherical portion, said chamber having an arcuately curved outer peripheral wall Whose center is removed from the center oi said rotary shaft and'curved side walls, each vane having inner and outer edges curved both in vertical and horizontal directions to conform to the 

